US3703862A - Work pressure rolling assembly - Google Patents

Work pressure rolling assembly Download PDF

Info

Publication number
US3703862A
US3703862A US588571A US3703862DA US3703862A US 3703862 A US3703862 A US 3703862A US 588571 A US588571 A US 588571A US 3703862D A US3703862D A US 3703862DA US 3703862 A US3703862 A US 3703862A
Authority
US
United States
Prior art keywords
roll
extending
pressure
neck
outside
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US588571A
Other languages
English (en)
Inventor
Valentin Appenzeller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Eduard Kuesters Maschinenfabrik GmbH and Co KG
Original Assignee
Eduard Kuesters Maschinenfabrik GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Eduard Kuesters Maschinenfabrik GmbH and Co KG filed Critical Eduard Kuesters Maschinenfabrik GmbH and Co KG
Application granted granted Critical
Publication of US3703862A publication Critical patent/US3703862A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • F16C13/022—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle
    • F16C13/024—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle
    • F16C13/026—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle by fluid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B3/00—Presses characterised by the use of rotary pressing members, e.g. rollers, rings, discs
    • B30B3/005—Roll constructions
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06B—TREATING TEXTILE MATERIALS USING LIQUIDS, GASES OR VAPOURS
    • D06B23/00—Component parts, details, or accessories of apparatus or machines, specially adapted for the treating of textile materials, not restricted to a particular kind of apparatus, provided for in groups D06B1/00 - D06B21/00
    • D06B23/02—Rollers
    • D06B23/021—Compressive rollers
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06C—FINISHING, DRESSING, TENTERING OR STRETCHING TEXTILE FABRICS
    • D06C15/00—Calendering, pressing, ironing, glossing or glazing textile fabrics
    • D06C15/08—Rollers therefor
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/0006—Driving arrangements
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/02—Rolls; Their bearings
    • D21G1/0206—Controlled deflection rolls
    • D21G1/0213—Controlled deflection rolls with deflection compensation means acting between the roller shell and its supporting member
    • D21G1/022—Controlled deflection rolls with deflection compensation means acting between the roller shell and its supporting member the means using fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2340/00—Apparatus for treating textiles

Definitions

  • a Controlled deflection has a relationship of the 51 Im. Cl. ..B30b3/04 frame Structure which mounts it and the fell Structure [58] Field of Search ..29/116 AD; 100/162 B itself which ellews the internal beam of the fell to be anchored and the source of power to the shell of the roll to be located outside of the frame structure.
  • This invention relates to work pressure rolling assemblies of the type including a roll for pressure rolling the work, and means for controlling the deflection or beam flexure of this roll caused by its application of pressure to the work being pressure rolled.
  • one of the objects of the present invention is to provide a work pressure rolling assembly having deflection controlling means on the inside of a hollow work rolling roll, while at the same time permitting the application of rotary power to this roll by connecting it with a source of rotary power located on the outside of the necessary frame members.
  • Controlled deflection roll assemblies of the type disclosed by the previously mentioned Appenzeller U.S. Pat. No. 2,908,964, have been commercially successful and another object of the present invention is to permit the use of the principles disclosed by this patent while at the same time permitting the hollow roll of this kind of assembly to be driven directly from a location on the outside of the frame members required to mount the roll assembly.
  • an assembly of the type to which this invention relates must include a hollow roll having an outer work rolling surface and be subject to deflection when the latter is engaging, under pressure the work being pressure rolled.
  • the work must, of course, be in turn supported by another roll which may be either a plain solid roll or another assembly of the same type under discussion.
  • a beam is located within this hollow roll and it extends for at least the length of the work rolling surface of this roll, and means are supplied for applying variable pressure from this beam to the inside of the hollow roll at a location and in a direction providing a reaction to the deflection to which the hollow roll would otherwise be subjected.
  • this means may be adjusted to keep the effective work rolling surface on the outside of the hollow roll truly linear, and sometimes it may be adjusted so that this surface is either concave or convex, depending upon the results desired.
  • the inside of the hollow roll must form a space permitting the beam inside of it to deflect when stressed by the pressure of the above-described means. All structural metals are elastically flexible and, therefore, something must deflect under the work rolling pressure, this being the beam on the inside of the hollow roll in roll assemblies of the type herein involved.
  • the outer working surface of the hollow roll then either deflects not at all, or more or less depending on the force provided in opposition to its normal deflection tendency under working conditions, by the pressure applying means on the inside of the roll.
  • the present invention is based on the novel concept of proportioning the beam, or of provid-' ing it with an extension rigidly connected with its beam length, so that it projects axially from one end of the roll far enough to be engaged by means for holding the beam against rotation.
  • this means may be located outside of one or another of the necessary frames.
  • the hollow roll itself at least at one end must be provided with a roll neck, or other extension, projecting axially far enough to be engaged by a rotative powering means, it also being possible to locate this rotative powering means on the outside of one or another of the two necessary frame members.
  • one end of a roll assembly incorporating the present invention is like the solid roll constructions of the Love U.S. Pat. No. 864,660 and the Gautschi U.S. Pat. No. 977,725, permitting direct application of rotary power outside of the frame members to the pressure rolling roll at any desired axial distance from its end, while the other end of the assembly has the beam projecting axially from it, or an extension of this beam, permitting the beam to be anchored against rotation at any axial distance desired outside of the frame members.
  • This new arrangement permits both the beam to be rotatively locked and the pressure rolling roll to be rotatively driven from locations on the outsides of the two frame members and, therefore, avoids all of the complexities involved by a rotary driving arrangement located between these frames. This is effected without sacrificing the advantages of the hollow roll arrangement having inside of it the means for controlling its deflection by transmitting the force to the beam located on the inside of the roll.
  • FIG. 1 is a side view showing a side of the frame and the two rolls between which the work is pressure rolled,
  • FIG. 2 is a front view of FIG. 1 on a somewhat reduced scale
  • FIG. 3 is a longitudinal section taken on a vertical plane through the work pressure rolling assembly or lower roll of FIG. 1, this being on almost the same scale as FIG. 1;
  • FIG. 4 is an enlarged scale cross-section taken on the line 4-4 in FIG. 3;
  • FIG. 5 reveals a detail on a greatly enlarged scale, shown by the right-hand end of FIG. 3;
  • FIG. 6 is a cross-section taken on the line 66 in FIG. 3, this view being on a further enlarged scale relative to FIG. 3;
  • FIG. 7 is a longitudinal section taken on the line 7-7 in FIG. 6 with the beam and its projecting end shown in elevation;
  • FIG. 8 is a longitudinal section taken on the line 88 in FIG. 6;
  • FIG. 9 is like FIG. 8, but is taken on the line 99 in FIG. 6 with the beam and its projecting end shown in elevation;
  • FIG. 10 is a longitudinal section on a vertical plane of a work pressure rolling assembly involving a modification relative to the construction shown by FIG. 3.
  • FIGS. 1 and 2 show the two necessary frame members or sides 1 and 2, these journaling by suitable bearings an upper roll 3 of the conventional solid type. It can easily be provided with means to rotate it directly by power applied outside of the frame members.
  • the frame members 1 and 2 include vertically swinging arms 4 and 5 which serve to mount the work pressure rolling assembly exemplifying the present invention. Hydraulic piston and cylinder assemblies 6 and 7 can swing these arms 4 and 5 upwardly and provide the rolling pressure.
  • the work pressure rolling assembly itself is indicated generally at 8 in FIGS. 1 and 2, and is shown in detail by FIGS. 3 through 9.
  • This work pressure rolling assembly includes the hollow roll 9 having an outer work rolling surface shown in this instance as comprising an elastically deformable covering 10 such as might be used when sizing is to be pressure-rolled on a web of material under relatively high pressure and demanding a narrowly restricted range of coating thickness tolerance transversely of the web.
  • the beam 11 is located within the roll 9 and extends at least for the length of the working portion of the surface 10 to meet the conditions for which it is provided.
  • the means for applying the variable pressure from this beam 11 to the inside of the roll 9 at the location and in a direction providing a reaction to the deflection of this roll 9, in this instance follows the principles of the previously mentioned Appenzeller US. Pat. No. 2,908,964. Although not shown, the general principles of the previously mentioned Specht US. Pat. No. 2,395,915 might possibly be substituted.
  • the beam 11 and the roll 9 have co-operating side seals 12 and end seals 13.
  • the outside diameter of the beam 11 is somewhat smaller than the inside diameter of the hollow roll 9 and the seals 12 and 13 divide the resulting space into upper and lower chambers.
  • Liquid under pressure such as lubricating or other oil from a pressure pump, is fed to the upper chamber through an inlet passage 14 so as to hydraulically apply a uniform pressure to the inside of the hollow roll 9 opposite to the roll 3 and the work passing between these two.
  • a passage 15 serves to exhaust liquid leaked through the seals.
  • the seals need not be absolutely fluid-tight, and that they may be made deliberately to leak more or less so that a flow of liquid is established through the assembly, sometimes done to permit roll temperature control for example.
  • the leakage rate must be adjusted to the capacity of the pump (not shown) to keep the upper chamber at the hydraulic pressure selected to provide the desired control of the shape of the roll 9 where it forms the working pass with the roll 3.
  • the beam 11 projects axially to the right from and beyond the right-hand end of the roll 9 far enough to be engaged by a means 16 for holding the beam 11 against rotation.
  • this beam end 11a which might be called more properly an extension 1 la of the beam since it is beyond the portion of the beam under beam stress, is so long that it extends through and beyond the frame 4.
  • This means 16 is not shown in FIGS. 1 and 2, but it is to be understood that it may comprise any kind of anchor or lock to prevent rotation of the beam.
  • it may be a bracket keyed to the projecting end 11a and secured against rotation or swinging by being fastened to the arm 4.
  • the ho]- low roll 9 is provided with a roll neck 9a projecting axially far enough outwardly or to the left to be engaged by any suitable rotative powering means.
  • the extreme end portion of the neck which forms a drive shaft S is shown as being provided with a keyway 9b.
  • the hollow roll 9 can be driven in the same manner as though it were either a solid roll as conventionally used or as would be the solid roll in the pressure work rolling assembly shown by the Love and Gautschi patents previously identified. Because the beam extension 11a projects through the end of the roll 9 so that it may be anchored against rotation independently with respect to the roll neck 9a, the new assembly accommodates the more advantageous principles of the Specht and Appenzeller patents, also previously identified.
  • the beam ends form seats 11b which are joumaled by the hollow roll 9 through self-aligning bearings 17 located inside of the roll 9. These bearings are located so that the beams unsupported span extends for at least the length of the working surface of the roll 9. With hydraulic pressure in the chamber above the seals 12 these bearings are loaded in an opposite direction, or downwardly, and the beam span flexes downwardly with the lower chamber providing clearance. As shown, the beam is positioned with its axis offset upwardly from the roll axis so that this clearance is increased by the extent of this offset.
  • the roll 9 has a second roll neck 9c projecting from its right-hand end, this neck being hollow and having an inside diameter proportioned relative to the diameter of the beam extension 11a, to define therebetween space large enough to permit angular motion of the extension 11a which results when the beam 11 deflects.
  • Both necks 9a and 9c are joumaled to the arms 4 and 5 through self-aligning rotary bearings 18.
  • All bearings are shown as self-aligning bearings of the anti-friction type which are preferred for actual use.
  • Such antifriction bearings embody rolling elements such as balls, rollers, or the like.
  • the roll 9 Without hydraulic pressure in the passage 14 and therefore in the upper chamber of the assembly, the roll 9 will be subject to beam flexure deflection when the cylinders 6 and 7 apply pressure to force the roll assembly upwardly against the reaction of the vertically fixed roll 3.
  • the self-aligning bearings 17 and 18 will accommodate all angular deflections of the two roll necks of the hollow roll relative to the frame members and the beam.
  • the beam 11 With the introduction of hydraulic pressure through the passage 14, a reaction is provided removing the beam flexure more or less, causing the upper surface of the roll 9 to become less concave or perhaps convex but in most cases linear, but as required by the operations under way in any event.
  • the beam 11 carries the beam stress and it will be subjected to beam flexure and consequent deflection downwardly, the lower chamber forming room for such deflection.
  • This causes angular motion of the necks or end portions 11b, accommodated by the self-aligning bearings 17, while the space between the beam end or extension 11a and the inside of the roll neck 90 provides room for angular motion of this part 11a.
  • the two roll necks 9a and 90 extending outwardly from the hollow roll 9 act to carry the forces and may be subject to angular deflection or beam flexure, but any resulting deflections are accommodated by the self-aligning bearings 18. Such deflection does not affect the portion of the hollow roll controlled by the hydraulic pressure.
  • FIG. 10 illustrates the fact that the principles of the invention may be used in other forms.
  • the beam extension 11a here marked 11a, is made much more massive and it is this beam extension that is joumaled by the bearing 18 which corresponds in location to the bearing 18 in FIG. 3.
  • the outer end of the beam or beam extension 11a will, of course, be locked against rotation.
  • the necessary longitudinally extending seals are not shown, but the equally necessary end seals 22 are shown as comprising elastically deformable nonmetallic ring elements. Leakage outwardly beyond the ring element at the right-hand end of the beam 11 in both forms is prevented by a ring seal 23 which is elastically deformable in a radial direction. Radial motion must be accommodated because the beam extension 11a must be able to deflect angularly when the beam 11 deflects in this instance.
  • the end of the roll of this FIG. 10 example which does not have a roll neck, is provided with an end member 20' which takes the place of the flange 20 of the first example, which is annular and has an inside diameter forming a space adequate for deflection of the beam extension 11a.
  • FIGS. 6 through 9 where it can be seen that at each end of the beam 11 the end seals 13 are in the form of metal strips positioned in channels 24 formed in a collar 25 positioned between the end of the beam 11 and the adjacent bearing 17. These channels and the sealing strips extend from locations substantially registering with the side seals 12 diagonally upwardly towards each other so that the ends of the strips meet at the vertical centerline of the collar 25, the strips having mitered ends 13a which abut each other at this point.
  • the strips are held in the channels by having recesses 13b engaged by cap screws 26 screwed into bores 27 extending radially inwardly from the collars periphery so that the inner ends of the screws are in the recesses 13b.
  • the latter are large enough to permit some movement of the strips 13 and the latter are urged outwardly towards the bearing 17 by compression springs 28 located in bores extending axially from the bottoms of the channels 24.
  • a flat annular bearing plate 29 is located between the collar 25 and the bearing 17 and against which the seals 13 are resiliently pressed by the springs 28.
  • the collar 25 itself is secured to the end of the beam 1 l by cap screws 30, the lower portion of the collar 25 having radially projecting nylon plugs 31 to assist in maintaining the collar 25 concentric with the inside of the roll 9.
  • the collar 25 at these diametrically opposite locations has radial channels 32 formed therein which merge with the adjacent portions of the channels 24 and in which radially projecting sealing strips 33 are located. These strips 33 are pressed outwardly by compression springs 34 located in the bottom of the channels 32 and the lower ends of the longer strips 13 bear on these strips 33.
  • the new roll assembly comprises the beam 11 having the bearing seats 1 lb on or at its ends and the extension or shaft 11a projecting axially beyond what in the drawings is the right-hand one of the seats.
  • the hollow work rolling roll 9 which is subject to deflection when engaging the work being pressure rolled, is tubular to avoid complicated fabrication.
  • the roll encircles the beam and the seats 11b, and defines the space therearound, the shaft lla projecting axially beyond the end of the roll adjacent thereto.
  • the self-aligning rotary bearings 17 on the seats 11b journal the beam and roll together.
  • at least one roll neck, 9a for example in FIG. 3 projects axially from the other end of the roll from which the shaft 11a projects.
  • This roll neck has the bearing 18 and extends further axially to permit it to be coupled to a source of rotary power beyond its bearing seat, as illustrated by the keyway 9b.
  • Means must, of course, be provided for applying the antbdeflection pressure. Preferably this is done by providing the seals 12 and 13 to define a chamber between the beam and the roll opposing the rolls area of deflection and into which hydraulic liquid under pressure may be introduced and maintained.
  • the roll neck 90 which also has a seat for the bearing 18 at that end, this neck encircling the shaft lla while providing clearance for the latter to deflect, the shaft continuing on outwardly so that its end may be locked against rotation.
  • the second bearing seat is provided by the shaft 110 itself, it being made sufficiently massive in this instance to transmit the rolling pressure to the roll assembly through the adjacent bearing 17.
  • the bearing 17 may be installed on the necks of the beam to form a subassembly which is inserted endwise into the hollow roll 9.
  • the interior of this hollow roll 9 should be smoothly finished to reduce the sliding friction between the side seals, held stationary by the beam because fixed to the latter, and the inside of the hollow roll.
  • the nylon plugs 31 previously referred to, provide bearing members sliding easily on the drums inside during insertion of the subassembly of the beam and its bearings and other parts. This prevents damage to the smooth inside of the hollow drum during assembling operations.
  • a work pressure rolling assembly including interspaced frame members, a hollow roll extending transversely between said members with its outside engagable by work between the members, a roll neck connected to one end of said roll for rotating the latter and extending axially therefrom through the adjacent one of said members to the latters outside, a rotary bearing connecting said neck to said adjacent member, the end of the roll to which this neck is connected being closed and the other end of the roll having an axially extending opening, interspaced rotary bearings on the inside of said roll adjacent to its ends, a deflectable beam inside of said roll and connected thereto by said interspaced bearings and spaced from the rolls inside between these bearings to permit the beam to deflect therebetween, one end of this beam terminating short of the rolls closed end and the other end of the beam having an extension for holding the beam against rotation and extending therefrom through said opening and through the other of said members to the latters outside, means for connecting said other end of said roll rotatively to said other of saidmembers, said roll being deflectable when
  • said means for connecting said other end of said roll to said other of the said members comprises a second roll neck connected to the said roll at its said other end and extending through this other member and a rotary bearing connecting this second roll neck to this other member, this second roll neck having an axially extending opening through which said beam extension projects.
  • a work pressure rolling assembly including interspaced frame members, a hollow roll that deflects when stressed, means for rotatively connecting said roll transversely to said members with the roll positioned so its outside is adapted to be engaged by work between the members, means extending axially from said roll through one of said members to the outside thereof for rotating the roll, a beam extending axially inside of said roll and which is also deflectable when stressed, means free from at least the longitudinal central portion of said roll for rotatively interconnecting said beam and the roll's inside at positions on both sides of the rolls said central portion, said beam being spaced radially from the rolls inside so the beam and roll can deflect relative to each other for at least substantially the extent of the rolls said central portion, means for applying pressure between said beam and the inside of the rolls said central portion for causing relative deflection of the roll and beam, one end of the roll having an axially extending opening, and an extension connecting with said beam and extending therefrom through said opening and the adjacent one of the frame members to the outside of the latter for holding
  • a work pressure rolling assembly including interspaced frame members, a deflectable hollow roll extending transversely between said members and having an outside work-engaging portion between its ends for applying rolling pressure along one side of the roll, a roll neck for mounting one end of said roll and rigidly extending axially from that one end of the roll through one of said frame members to the latters outside and having an outer end which is accessible from said outside, a bearing rotatively connecting said neck to said member, interspaced self-aligning rotary bearings inside of said roll and respectively positioned outwardly from the opposite ends of said work-engaging portion of this roll, a deflectable beam inside of said roll and mounted by the latter through said interspaced bearings and spaced from the rolls inside between these bearings to permit the beam and said roll to deflect relative to each other between these hearings, one end of said beam terminating short of said neck's accessible end and the other end of this beam having an extension for holding the beam against rotation and extending therefrom through the other end of said roll and through the other of said frame members
  • first bearing means extending about said roll necks and rotatably supporting said roll.necks and roll shell
  • a center shaft extending along the interior of said portion of said shell and beyond opposite ends of said portion and having fluid pressure means adapted to apply nip correcting pressure to the inside of said portion of said roll shell,
  • a controlled deflection roll assembly forming a pressure nip portion between its ends with a second roll comprising:

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Textile Engineering (AREA)
  • Paper (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Treatments Of Macromolecular Shaped Articles (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)
  • Treatment Of Fiber Materials (AREA)
US588571A 1963-06-25 1966-10-21 Work pressure rolling assembly Expired - Lifetime US3703862A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEK50053A DE1243965B (de) 1963-06-25 1963-06-25 Walze fuer die Druckbehandlung von Warenbahnen, wie Papier- und Textilbahnen

Publications (1)

Publication Number Publication Date
US3703862A true US3703862A (en) 1972-11-28

Family

ID=7225468

Family Applications (1)

Application Number Title Priority Date Filing Date
US588571A Expired - Lifetime US3703862A (en) 1963-06-25 1966-10-21 Work pressure rolling assembly

Country Status (7)

Country Link
US (1) US3703862A (de)
BR (1) BR6460327D0 (de)
DE (1) DE1243965B (de)
ES (1) ES301353A1 (de)
FI (1) FI42786B (de)
FR (1) FR1403210A (de)
GB (1) GB1074936A (de)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3879827A (en) * 1973-06-15 1975-04-29 Escher Wyss Ltd Roll for a rolling mill
US3919753A (en) * 1973-11-22 1975-11-18 Escher Wyss Ltd Roll
US3949455A (en) * 1974-04-10 1976-04-13 Escher Wyss Limited Flexure-compensating roll
US3997952A (en) * 1975-01-29 1976-12-21 Escher Wyss Limited Roll for a rolling mill
US4048701A (en) * 1975-11-04 1977-09-20 Escher Wyss Limited Deflection compensating roll
DE2902955A1 (de) * 1979-01-22 1980-07-24 Escher Wyss Ag Durchbiegungseinstellwalze
US4325170A (en) * 1979-09-24 1982-04-20 Eduard Kusters Deflection controlled cylinder
US4416137A (en) * 1981-03-20 1983-11-22 Davy-Loewy Limited Roll construction
US4440077A (en) * 1981-05-07 1984-04-03 J. M. Voith Gmbh Press roller with adjustable bending characteristics
DE3329595A1 (de) * 1983-08-16 1985-03-07 Küsters, Eduard, 4150 Krefeld Walze fuer einen folienziehkalander o. dgl.
DE3343313A1 (de) * 1983-11-30 1985-06-05 J.M. Voith Gmbh, 7920 Heidenheim Walze zur behandlung von bahnen, vorzugsweise papierbahnen
EP0374381A2 (de) * 1988-12-23 1990-06-27 Eduard Küsters Maschinenfabrik GmbH & Co. KG Walze
EP0399976A2 (de) * 1989-05-22 1990-11-28 Valmet Paper Machinery Inc. Verfahren zur Steuerung der Temperatur einer Walze mit anpassbarer Biegelinie und Regelungssystem zur Durchführung des Verfahrens
US5111566A (en) * 1990-06-25 1992-05-12 Sulzer Escher Wyss Ag Controlled deflection roll
JP2008524034A (ja) * 2004-12-20 2008-07-10 アントリッツ キュスタース ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト 薄いシートを製造及び／又は加工するためのカレンダ
WO2021127803A1 (zh) * 2019-12-23 2021-07-01 宝利泰橡胶科技扬州有限公司 一种均匀轧车

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3506182A1 (de) * 1985-02-22 1986-09-04 Küsters, Eduard, 4150 Krefeld Walze mit antriebseinrichtung
BE1004291A3 (fr) * 1989-07-17 1992-10-27 Solvay Cylindre de calandrage a compensation de flexion.

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1799775A (en) * 1928-10-26 1931-04-07 Beloit Iron Works Suction roll
US2908964A (en) * 1957-01-18 1959-10-20 Kuesters Eduard Pressure treatment of material
US3023695A (en) * 1958-07-04 1962-03-06 Textilmaschinen Eduard Kusters Roll arrangements for subjecting strip or web material to pressure treatment
US3037557A (en) * 1960-07-06 1962-06-05 Time Inc Rotary vacuum cylinder
US3119324A (en) * 1960-08-29 1964-01-28 Beloit Iron Works Controlled deflection roll
US3146160A (en) * 1960-08-01 1964-08-25 Beloit Iron Works Roll with adjustable deflection means
US3196520A (en) * 1962-11-10 1965-07-27 Kuesters Eduard Maschf Tubular roller with carrier core and division of the gap between the roller and core into longitudinal chambers
US3276102A (en) * 1964-01-24 1966-10-04 Beloit Corp Adjustable crown roll
US3286325A (en) * 1964-01-24 1966-11-22 Beloit Corp Support and drive for controlled crown roll
US3290897A (en) * 1965-05-26 1966-12-13 Farrel Corp Drive for shell type rolls

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1799775A (en) * 1928-10-26 1931-04-07 Beloit Iron Works Suction roll
US2908964A (en) * 1957-01-18 1959-10-20 Kuesters Eduard Pressure treatment of material
US3023695A (en) * 1958-07-04 1962-03-06 Textilmaschinen Eduard Kusters Roll arrangements for subjecting strip or web material to pressure treatment
US3037557A (en) * 1960-07-06 1962-06-05 Time Inc Rotary vacuum cylinder
US3146160A (en) * 1960-08-01 1964-08-25 Beloit Iron Works Roll with adjustable deflection means
US3119324A (en) * 1960-08-29 1964-01-28 Beloit Iron Works Controlled deflection roll
US3196520A (en) * 1962-11-10 1965-07-27 Kuesters Eduard Maschf Tubular roller with carrier core and division of the gap between the roller and core into longitudinal chambers
US3276102A (en) * 1964-01-24 1966-10-04 Beloit Corp Adjustable crown roll
US3286325A (en) * 1964-01-24 1966-11-22 Beloit Corp Support and drive for controlled crown roll
US3290897A (en) * 1965-05-26 1966-12-13 Farrel Corp Drive for shell type rolls

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3879827A (en) * 1973-06-15 1975-04-29 Escher Wyss Ltd Roll for a rolling mill
US3919753A (en) * 1973-11-22 1975-11-18 Escher Wyss Ltd Roll
US3949455A (en) * 1974-04-10 1976-04-13 Escher Wyss Limited Flexure-compensating roll
US3997952A (en) * 1975-01-29 1976-12-21 Escher Wyss Limited Roll for a rolling mill
US4048701A (en) * 1975-11-04 1977-09-20 Escher Wyss Limited Deflection compensating roll
DE2902955A1 (de) * 1979-01-22 1980-07-24 Escher Wyss Ag Durchbiegungseinstellwalze
US4325170A (en) * 1979-09-24 1982-04-20 Eduard Kusters Deflection controlled cylinder
US4416137A (en) * 1981-03-20 1983-11-22 Davy-Loewy Limited Roll construction
US4440077A (en) * 1981-05-07 1984-04-03 J. M. Voith Gmbh Press roller with adjustable bending characteristics
DE3329595A1 (de) * 1983-08-16 1985-03-07 Küsters, Eduard, 4150 Krefeld Walze fuer einen folienziehkalander o. dgl.
DE3343313A1 (de) * 1983-11-30 1985-06-05 J.M. Voith Gmbh, 7920 Heidenheim Walze zur behandlung von bahnen, vorzugsweise papierbahnen
EP0374381A2 (de) * 1988-12-23 1990-06-27 Eduard Küsters Maschinenfabrik GmbH & Co. KG Walze
EP0374381A3 (de) * 1988-12-23 1993-01-13 Eduard Küsters Maschinenfabrik GmbH & Co. KG Walze
EP0399976A2 (de) * 1989-05-22 1990-11-28 Valmet Paper Machinery Inc. Verfahren zur Steuerung der Temperatur einer Walze mit anpassbarer Biegelinie und Regelungssystem zur Durchführung des Verfahrens
EP0399976A3 (de) * 1989-05-22 1991-05-08 Valmet Paper Machinery Inc. Verfahren zur Steuerung der Temperatur einer Walze mit anpassbarer Biegelinie und Regelungssystem zur Durchführung des Verfahrens
US5111566A (en) * 1990-06-25 1992-05-12 Sulzer Escher Wyss Ag Controlled deflection roll
JP2008524034A (ja) * 2004-12-20 2008-07-10 アントリッツ キュスタース ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト 薄いシートを製造及び／又は加工するためのカレンダ
WO2021127803A1 (zh) * 2019-12-23 2021-07-01 宝利泰橡胶科技扬州有限公司 一种均匀轧车

Also Published As

Publication number Publication date
FR1403210A (fr) 1965-06-18
FI42786B (de) 1970-06-30
DE1243965B (de) 1967-07-06
BR6460327D0 (pt) 1973-01-11
GB1074936A (en) 1967-07-05
ES301353A1 (es) 1965-06-01

Similar Documents

Publication Publication Date Title
US3703862A (en) Work pressure rolling assembly
CA1263551A (en) Pressure roll for use in calenders or the like
US3885283A (en) Press roll
CA1059567A (en) Hydrostatic support arrangement
CA1189370A (en) Temperature control for shell type rolls
FI106976B (fi) Itsekuormittava taipumasäädetty tela
US4837907A (en) Self-loading controlled deflection roll
US4796452A (en) Setting device for adjusting the position of a roll
FI79177B (fi) Boejningsreglerad vals.
US4856154A (en) Method and device in an adjustable crown roll
US4962577A (en) Work roll with improved support and lubricating system for an hydraulically supported roll
US5495798A (en) Adjustable-crown roll
US3286325A (en) Support and drive for controlled crown roll
FI69684C (fi) Tryckbehandlingsvals med en hydraulisk stoettning
JP4081261B2 (ja) 製紙／製板機または仕上げ機用ロール外部支持すべり軸受装置
US4850088A (en) Self-loading controlled deflection roll
US4995147A (en) Roll having improved transverse end seals
US5193258A (en) Self-loading controlled deflection roll
US6796929B2 (en) Self-adjusting deflection controlled roll
US3120174A (en) Apparatus for resisting roll deflection
US4891874A (en) Self loading controlled deflection roll
US5788619A (en) Hydrostatic self-loading controlled deflection roll
US6203480B1 (en) Pressure processing roll
US5474656A (en) Equal lift self-loading controlled deflection roll and method for operating same
US3418703A (en) Antideflection roll with non-rotating beam and lever supports